WO2011035677A1 - Rotary pump - Google Patents
Rotary pump Download PDFInfo
- Publication number
- WO2011035677A1 WO2011035677A1 PCT/CN2010/076415 CN2010076415W WO2011035677A1 WO 2011035677 A1 WO2011035677 A1 WO 2011035677A1 CN 2010076415 W CN2010076415 W CN 2010076415W WO 2011035677 A1 WO2011035677 A1 WO 2011035677A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- cam
- chamber
- sealing
- pump according
- Prior art date
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0827—Vane tracking; control therefor by mechanical means
- F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2250/00—Geometry
- F04C2250/20—Geometry of the rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
- F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
- F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
Definitions
- the present invention relates to a rotor pump, and more particularly to a rotary rotor pump. Background technique
- High pressure gases such as air can be used in a wide range of applications such as engine boosting, pneumatic tools, high pressure cleaning appliances and instrumentation power.
- the compression of the gas is performed by a motor driving a piston in a cylinder to reciprocate, wherein a normal pressure gas is first supplied into a closed space formed by the cylinder and the piston, and the piston is continuously moved to reduce the sealing.
- the atmospheric gas is compressed into a high pressure gas, and the compressed high pressure gas is then stored in a gas storage tank for standby.
- the existing compression device is usually a piston type, and when the piston reciprocates, a top dead center and a bottom dead point are generated, that is, a reciprocating position of the piston moving direction, so the existing piston type compression device is relatively smooth, and will be generated. Larger noise. Furthermore, in the existing compression device, lubricating fluid must be provided in the cylinder to reduce the friction so that the piston can reciprocate smoothly in the cylinder. When the lubricating fluid is insufficient or the lubricating fluid is insufficient, the piston and the cylinder are generated. Extreme friction, the lighter affects the compression efficiency, and the heavy one may damage the cylinder structure or the temperature is too high, causing the piston and the cylinder to sinter.
- An object of the present invention is to provide a rotor type pump to solve various problems in the prior art described above.
- the present invention provides a rotor pump comprising a body, a rotor, at least one cam and a sealing unit.
- the body has a chamber, an air inlet portion and an air outlet portion.
- the rotor shaft is disposed in the chamber, the rotor having a circumferential surface having at least one convex surface that closely contacts the inner surface of the chamber.
- Each cam There is a cam surface, and the at least one cam rotates in cooperation with the rotor.
- the sealing unit has a sealing portion and at least one concentric portion, the sealing portion contacting the circumferential surface of the ring, the at least one concentric portion contacting the cam surface, and the sealing portion moves with the at least one homogenous portion.
- the at least one collet portion moves according to the corresponding cam surface, such that the sealing portion of the same crucible moves continuously in close contact with the circumferential surface of the ring, and the gas enters the chamber from the inlet portion
- the sealing portion, the convex surface and the inner surface of the chamber form a substantially closed space
- the rotating rotor continuously compresses the gas in the chamber, in the chamber When the gas is compressed to a set pressure, it is led out by the gas outlet.
- the smooth convex surface of the rotor is in close contact with the inner surface of the chamber, and the gas in the chamber is compressed by rotation.
- the rotor of the present invention does not need to reciprocate as the existing piston. There will be no dead spots, so it is smooth and not easy to produce noise.
- the rotor type pump of the present invention can form a lubricating and heat-resistant coating on the surface of the rotor without a lubricating fluid, and the rotor type pump of the present invention has an extremely large amount of compression and compression efficiency.
- Figure 1A is a cross-sectional view showing the first embodiment of the rotor type pump of the present invention
- Figure 1B is a cross-sectional view taken along line 1B-1B of Figure 1A;
- Figure 1C shows a cross-sectional view taken along line 1C-1C of Figure 1A;
- FIGS. 2 to 4 are views showing the compression stroke of the rotor type pump of the first embodiment of the present invention
- Figure 5 is a view showing the cooperation of a sealing unit having a linear guiding device with a rotor and a cam in the rotor type pump of the first embodiment of the present invention
- Figure 6 is a schematic view showing a second embodiment of the rotor type pump of the present invention.
- Figure 7 is a schematic view showing a return valve of a rotor type pump and a piston structure of a second embodiment of the present invention
- 8 to 10 are views showing the compression stroke of the rotor type pump of the second embodiment of the present invention
- Figure 11 is a schematic view showing a rotor type pump of a third embodiment of the present invention.
- the rotor pump of the present invention comprises a body, a rotor, at least one cam and a sealing unit.
- the body has a chamber, an air inlet portion and an air outlet portion.
- the sealing unit has a sealing portion and at least one identical portion.
- the rotor pump 1 includes a body 11, a rotor 12, two cams 13, a rotating shaft 14, and a sealing unit 15.
- the body 11 has a chamber 111, two receiving spaces 112, an air inlet portion 113 and an air outlet portion 114.
- the receiving spaces 112 are disposed on two sides of the chamber 111. It can be understood that the body 11 can include only a receiving space 112 disposed on one side of the chamber 111.
- the chamber 111 is a hollow cylindrical space. It should be noted that the chamber 111 and the rotor 12 may have any cooperating shape, that is, the shape of the chamber 111 is not limited to a hollow shape. Cylindrical.
- the gas enters the chamber 111 from the inlet portion 113.
- the outlet portion 114 has a check valve 115 and a line 116.
- the check valve 115 communicates with the inside of the chamber 111 to allow gas to pass through the chamber 111. It is derived and cannot be reversely entered into the chamber 111, and the line 116 is connected to the check valve 115 for guiding the gas discharged from the chamber 111.
- the air outlet portion 114 includes an outer passage 117 and an inner passage 118.
- the check valve 115 is connected to the outer passage 117.
- the outer passage 117 is opened from a side wall of the body 11 to a set depth, and the inner passage 118 communicates with the outer passage 117 and opens in the direction of the chamber 111 to open the chamber 111 (formed) A substantially L-shaped channel).
- the cross-sectional dimension of the inner passage 118 is larger than the cross-sectional dimension of the outer passage 117, and the inner passage 118 is opened to communicate with the peripheral portion of the chamber 111.
- the rotor 12 is axially disposed in the chamber 111.
- a section of the rotor 12 is cam-shaped, which operates at the center of the design.
- the rotor 12 has a circumferential surface 121 having at least one convex surface 122 that closely contacts the inner surface of the chamber 111.
- the cams 13 are connected to the rotor 12 via the rotating shaft 14.
- the rotor 12 and the cam 13 are of a coaxial cam type, and the rotor 12 has the same line shape as the cam 13.
- Each of the cams 13 has a cam surface 131 which cooperates with the rotor 12 to rotate (in the present embodiment, the same rotation). At least one of the rotor 12 and the cam 13 may have a coating.
- the coating layer 123 is made of Teflon.
- the coating layer 123 can improve the lubrication degree and the adhesion of the convex surface 122 to the inner surface of the chamber 111, and can reduce the friction between the rotor 12 and the inner surface of the chamber 111, thereby improving the compression efficiency and not damaging the cavity. The structure of the chamber 111 and the sintering of the rotor 12 from the chamber 111 are avoided.
- the rotary shaft 14 connects the rotor 12 and the cams 13.
- the rotating shaft 14 is connected to a rotating power source (not shown) through which the rotating power source 14 drives the rotor 12 and the cams 13.
- the rotating shaft 14 is located on the axial center of the rotor 12 and the cams 13, that is, the rotor 12 and the cams 13 are coaxially disposed.
- the rotor pump 1 may further include at least one weight element 16 for balancing the rotation to increase the rotational speed.
- the at least one weight element 16 is disposed on the rotating shaft 14.
- the rotation can be balanced, and the rotational speed can be increased, thereby
- the at least one weight element 16 can also stabilize the rotation of the rotor 12 and the cams 13.
- the rotor pump 1 may further include a plurality of weight elements disposed on the rotating shaft 14 and located on two sides of the rotor 12 (two respectively located on the body 11) side) .
- the sealing unit 15 has a sealing portion 151 and a second portion.
- the sealing portion 151 contacts the circumferential surface 121, and the equivalent portion 152 contacts the cam faces 131, respectively, and the sealing portion 151 moves in unison with the equivalent jaw portion 152.
- the sealing portion 151 is passed through the body 11 and contacts the circumferential surface 121 of the rotor 12, and the sealing portion 151 is located between the air inlet portion 113 and the air outlet portion 114.
- the equivalent turns portion 152 are respectively passed through the body 11 and respectively contact the cam faces 131.
- the base portion 153 connects the sealing portion 151 and the equivalent jaw portion 152, and the sealing portion 151 is located between the equivalent jaw portions 152.
- the return mechanism 154 is a spring mechanism.
- the reply mechanism 154 The base portion 153 is coupled, and the return mechanism 154 provides a pressure to keep the sealing portion 151 in close contact with the circumferential surface 121. It will be appreciated that the return mechanism 154 also provides a pressure to maintain the equivalent jaw portion 152 in intimate contact with the cam faces 131.
- the rotor 12 and the cams 13 are rotated, and the equivalent jaw portion 152 is moved in accordance with the corresponding cam surface 131 such that the sealing portion 151 of the same movement continues to closely contact the circumferential surface 121.
- the gas enters the chamber 111 from the inlet portion 113.
- the sealing portion 151, the convex surface 122 and the inner surface of the chamber 111 form a substantially closed space.
- the rotating rotor 12 continues to compress the gas in the chamber 111, and the gas in the chamber 111 is discharged from the venting portion 114 when compressed to a set pressure.
- the return mechanism 154 provides the sealing portion 151 - the leftward pressure, which continuously contacts the cam faces 131 and continues to move to the left, the sealing portion 151
- the equivalent portion 152 is displaced at the same time, so that the sealing portion 151 is simultaneously moved to the left.
- the convex surface 122 of the rotor 12 moves to the left in the same direction, and the displacement amount thereof and the displacement amount of the sealing portion 151 to the left are shifted.
- the return mechanism 154 provides the pressure of the sealing portion 151 to the left, so that the sealing portion 151 can continue to closely contact the circumferential surface 121.
- the rotor 12 and the cams 13 have the same rotational speed, and the shape of the cam surface 131 of the cams 13 matches the shape of the circumferential surface 121 of the rotor 12 (the rotor 12 and The cams 13 have the same line shape, and the cams 13 rotate with the rotor 12.
- the cross-sectional dimension of the inner passage 118 is larger than the cross-sectional dimension of the outer passage 117.
- the rotation of the rotor 12 can be controlled until the convex surface 122 completely covers the joint.
- the check valve 115 is opened when the opening of the inner passage 118 (also reaches the set pressure), and the compressed gas is led out of the chamber 111.
- the space of the chamber 111 can be fully utilized, thereby increasing the compression efficiency of the gas.
- the sealing unit 15 may further include at least one linear guiding device 155, each linear guiding device 155 including a linear bearing 156 and a guiding shaft 157, the linear bearing 156
- the pivot shaft 14 is pivoted and has a guiding portion 158.
- the guiding shaft 157 is disposed on one side of the sealing portion 151 and connected to the base portion 153, and moves along with the sealing portion 151 and the concentric portion 152 according to the guiding portion 158.
- the rotor pump 1 of the present invention can also be applied in a negative pressure environment (for example, to form a negative pressure environment or a vacuum state), that is, the rotor pump 1 of the present invention can be used as a "compression” or a reverse To "vacuum pressure”.
- the air inlet portion 113 is connected to a space or device (not shown) for forming a negative pressure environment or a vacuum state.
- the air intake space is A negative pressure state (relative to a space or device in which a negative pressure environment or a vacuum state is to be formed) is formed, and a space in a space or a device in which a negative pressure environment or a vacuum state is to be formed is sucked into the air intake space.
- the rotor 12 rotates to cover the intake portion 113 again (as shown in FIG. 1B), it is also prepared for the next gas suction. Procedure to achieve the effect of a negative pressure environment or a vacuum state.
- the rotor pump 2 includes a body 21, a rotor 22, a cam 23, two rotating shafts 24, a sealing unit 25, and a return mechanism 26.
- the body 21 has a chamber 211, an air outlet portion 212, a setting port 213 and an air inlet portion 213 formed between the air outlet portion 212 and the air inlet portion 214.
- the rotor type pump 2 of the second embodiment of the present invention includes at least one compression unit.
- the rotor pump 2 has a compression unit 20, and the compression unit 20 includes a chamber 211, an air outlet portion 212, a setting port 213, an air inlet portion 214, a rotor 22, and a cam 23.
- each of the chambers 211, an air outlet portion 212, a set port 213, and an air inlet portion 214 constitute a structure of a cylinder.
- the body 21 is a hollow cylinder. It can be understood that the body 21 can also be a structure having a hollow cylindrical chamber as shown in FIGS. 1A to 1C.
- the air outlet portion 212 has a check valve 215 and a pipeline 216.
- the check valve 215 communicates with the chamber 211 so that gas can be led out of the chamber 211 and cannot enter the chamber 211 in a reverse direction.
- the line 216 is connected to the check valve 215 for guiding the gas discharged from the chamber 211.
- the rotor 22 is axially disposed in the chamber 211 via a shaft 24 along the axis of the body 21 (also the axis of the chamber 211).
- the rotor 22 has a circumferential surface 221 having a convex surface 222 that abuts against the inner wall of the chamber 211.
- the rotor 22 and the cam 23 are of a different-axis conjugate wheel type (the rotor 22 and the conjugated cam 23 wheel type mutually compensated).
- the cam 23 is disposed on the other rotating shaft 24 and the axial line is substantially parallel to the axial line of the body 21, and the cam 23 has a cam surface 231. Wherein, at least one of the rotor 22 and the cam 23 may have a coating.
- the rotor 22 has a coating 223 and the cam 23 also has a coating 232.
- the cladding layers 223 and 232 are of Teflon material.
- the sealing unit 25 is disposed through the setting port 213 and between the rotor 22 and the cam 23.
- the sealing unit 25 is substantially perpendicular to the axial line of the cam 23 and the chamber 211 The direction of the axis line, wherein the sealing unit 25 and the setting port 213 have good Good close contact effect.
- the sealing unit 25 has a first portion 251 (ie, the at least one identical portion 152 in the first embodiment) and a second portion 252 (ie, the sealing portion 151 in the first embodiment).
- the first portion 251 contacts the cam surface 231.
- the first portion 251 and the second portion 252 are substantially T-shaped, and one end of the second portion 252 contacts the circumferential surface 221 of the ring.
- the returning mechanism 26 is coupled to the sealing unit 25 for providing a restoring force of the sealing unit 25 toward the cam 23.
- the returning mechanism 26 is a resilient member.
- the resilient member is a spring and is disposed between the cam 23 and the body 21 at the second portion 252 of the sealing unit 25.
- the rotor 22 and the cam 23 each have a rotational speed during operation, and the circumferential surface 221 of the rotor 22 and the cam surface 231 of the cam 23 are shaped according to the sealing unit.
- the size of the rotor 25, the rotational speed of the rotor 22 and the cam 23, and the distance between the rotor 22 and the cam 23 are designed to rotate with the rotor 22.
- the first portion 251 of the sealing unit 25 is based on the cam surface 231.
- the shape drives the sealing unit 25 to move toward the rotor 22 such that the second portion 252 of the sealing unit 25 continues to abut the circumferential surface 221.
- the compressed gas is led out of the chamber 211 (having different set pressures depending on different check valves); while the rotor 22 continues to rotate during the compression stroke, the convex surface 222 becomes incompletely obscuring the intake portion 214
- An air intake space 28 is formed in the chamber 211 (Figs. 9, 10), and the uncompressed gas enters the air intake space 28 from the air inlet portion 214, and the rotor 22 rotates to cover the air intake again.
- 214 proceed to the next Compression stroke.
- the rotor pump 2 of the present embodiment can also be applied in the formation of a negative pressure environment (for example, to shape In a negative pressure environment or a vacuum state, that is, the rotor pump 2 of the present embodiment can be used as a "compression” or a reverse "vacuum pressure".
- the air inlet portion 214 is connected to a space or device (not shown) for forming a negative pressure environment or a vacuum state. While the rotor 22 continues to rotate for the compression stroke, and the convex surface 222 does not completely cover the air inlet portion 214, the air intake space 28 in the chamber 211 continues to increase (as shown in FIGS. 9, 10).
- a negative pressure state (relative to a space or device for forming a negative pressure environment or a vacuum state) is formed in the intake space 28, and a space in the space or device to be formed into a negative pressure environment or a vacuum state is sucked into the intake space 28 .
- the rotor 22 rotates to cover the intake portion 214 again (Fig. 8)
- the next gas suction program is also prepared to achieve the effect of a negative pressure environment or a vacuum state.
- the return mechanism 26 may include a pressure valve 261 and a piston structure 262, wherein the pressure valve 261 is connected to the pipeline 216, and the piston structure 262 is connected thereto.
- the pressure-pressure valve 261 and the sealing unit 25 regulate the gas pressure passing through the pressure-regulating valve 261, and drive the piston structure 262 to interlock the sealing unit 25.
- the pressure required to supply the piston structure 262 can be maintained by the compressed gas generated by the compression. Wherein, after the compressed gas generated by each compression stroke is discharged to the pipeline 216, part of the gas passes through the pressure regulating valve 261 to the piston structure 262, and has the function of automatic air supply.
- the sealing unit 25 When the sealing unit 25 moves toward the rotor 22, the sealing unit 25 generates displacement by the thrust generated by the cam 23, and further changes the relationship of the gas pressure in the piston structure 262 to calculate the sealing unit 25.
- An optimum moving position when the sealing unit 25 moves toward the cam 23, the gas pressure in the rotor 22 and the piston structure 262 provides the sealing unit 25-thrust, and the return mechanism 26 also provides the sealing unit 25.
- the restoring force of the displacement to maintain the driven relationship of the sealing unit 25 and the cam surface 231.
- the displacement restoring force provided by the return mechanism 26 can reduce the friction between the sealing unit 25 and the rotor 22 to reduce wear and improve work efficiency.
- FIG. 11 there is shown a schematic view of a third embodiment of a rotor pump of the present invention.
- the rotor type pump 3 of the third embodiment has a plurality of (two) compression units 20.
- the compression unit 20 has a phase difference between the rotors 22, and the recovery mechanism 26 has a pressure valve 261 and a piston junction.
- the unit 262, the piston structure 262 of the return mechanism 26 can be coupled to the same pressure relief valve 261 (which can also be coupled to a different pressure relief valve), and the pressure regulating valve 261 regulates the distribution into the piston structure 262. gas pressure.
- the rotors 22 of the compression units 20 have a phase difference of 180 degrees.
- the upper rotor 22 contacts the inner wall of the chamber 211 on the left side
- the other rotor below the figure. 22 contacts the inner wall of the chamber 211 on the right side.
- the rotor pump 3 of the third embodiment has two compression units 20, and the compression units 20 have a phase difference between the rotors 22, so the compression units 20 completes the gas compression stroke interval for a period of time, thereby providing a more continuous, smoother, and more adequate compressed gas, or more efficiently enabling a space or device to achieve a negative pressure environment or vacuum.
- the rotor pump 3 of the third embodiment may have more compression units depending on the different needs of the different devices that connect the rotor pump 3.
- the smooth convex surface of the rotor is in close contact with the inner surface of the chamber of a body, and the gas in the chamber is compressed by rotation.
- the rotor of the present invention does not need to reciprocate as the existing piston. Exercise, there will be no dead spots, so it is smooth and not easy to produce noise.
- the rotor type pump of the present invention can form a lubricating and heat-resistant coating on the surface of the rotor without a lubricating fluid, and the rotor type pump of the present invention has an extremely large amount of compression and compression efficiency.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Abstract
Description
Claims
Priority Applications (8)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA2774107A CA2774107C (en) | 2009-09-23 | 2010-08-27 | Rotor type pump |
JP2012530115A JP5480387B2 (en) | 2009-09-23 | 2010-08-27 | Rotor pump |
AU2010297740A AU2010297740B2 (en) | 2009-09-23 | 2010-08-27 | Rotary pump |
KR1020127007004A KR101290849B1 (en) | 2009-09-23 | 2010-08-27 | Rotary pump |
EP10818371A EP2481929A1 (en) | 2009-09-23 | 2010-08-27 | Rotary pump |
MYPI2012001303A MY179758A (en) | 2009-09-23 | 2010-08-27 | Rotor type pump |
US13/381,527 US8684713B2 (en) | 2009-09-23 | 2010-08-27 | Rotor type pump |
ZA2012/01887A ZA201201887B (en) | 2009-09-23 | 2012-03-14 | Rotary type pump |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN2009101742169A CN102022320B (en) | 2009-09-23 | 2009-09-23 | Linked conjugate pump |
CN200910174216.9 | 2009-09-23 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011035677A1 true WO2011035677A1 (en) | 2011-03-31 |
Family
ID=43795382
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/CN2010/076415 WO2011035677A1 (en) | 2009-09-23 | 2010-08-27 | Rotary pump |
Country Status (10)
Country | Link |
---|---|
US (1) | US8684713B2 (en) |
EP (1) | EP2481929A1 (en) |
JP (1) | JP5480387B2 (en) |
KR (1) | KR101290849B1 (en) |
CN (1) | CN102022320B (en) |
AU (1) | AU2010297740B2 (en) |
CA (1) | CA2774107C (en) |
MY (1) | MY179758A (en) |
WO (1) | WO2011035677A1 (en) |
ZA (1) | ZA201201887B (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN108105092A (en) * | 2017-12-19 | 2018-06-01 | 珠海格力节能环保制冷技术研究中心有限公司 | Compressor |
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CN101105174A (en) * | 2007-07-06 | 2008-01-16 | 薛亮亮 | Low-power consumption rolling piston type refrigerating compressor |
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US154298A (en) * | 1874-08-18 | Improvement in rotary engines | ||
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JPS63189684A (en) * | 1987-02-03 | 1988-08-05 | Matsushita Electric Ind Co Ltd | Rotary compressor |
ATE346238T1 (en) * | 2000-07-10 | 2006-12-15 | Ea Technical Services Ltd | ROTARY PISTON FLUID DISPLACEMENT MACHINE |
TWI263762B (en) * | 2002-08-27 | 2006-10-11 | Sanyo Electric Co | Multi-stage compression type rotary compressor and a setting method of displacement volume ratio for the same |
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KR101234824B1 (en) * | 2005-01-18 | 2013-02-20 | 삼성전자주식회사 | Multi-stage compression type rotary compressor |
JP2009174461A (en) * | 2008-01-25 | 2009-08-06 | Daikin Ind Ltd | Compressor |
-
2009
- 2009-09-23 CN CN2009101742169A patent/CN102022320B/en not_active Expired - Fee Related
-
2010
- 2010-08-27 AU AU2010297740A patent/AU2010297740B2/en not_active Ceased
- 2010-08-27 JP JP2012530115A patent/JP5480387B2/en not_active Expired - Fee Related
- 2010-08-27 US US13/381,527 patent/US8684713B2/en not_active Expired - Fee Related
- 2010-08-27 WO PCT/CN2010/076415 patent/WO2011035677A1/en active Application Filing
- 2010-08-27 EP EP10818371A patent/EP2481929A1/en not_active Withdrawn
- 2010-08-27 MY MYPI2012001303A patent/MY179758A/en unknown
- 2010-08-27 KR KR1020127007004A patent/KR101290849B1/en active IP Right Grant
- 2010-08-27 CA CA2774107A patent/CA2774107C/en not_active Expired - Fee Related
-
2012
- 2012-03-14 ZA ZA2012/01887A patent/ZA201201887B/en unknown
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EP0008531A1 (en) * | 1978-08-18 | 1980-03-05 | Ronald Edward Smolinski | Rotary machine |
CN2156304Y (en) * | 1993-03-15 | 1994-02-16 | 殷参 | Driving device for plunger pump |
CN2558791Y (en) * | 2002-06-24 | 2003-07-02 | 汤科儿 | Axial through sliding-vane air compressor |
CN2767709Y (en) * | 2005-01-14 | 2006-03-29 | 战旗 | Two-stage compression type cam compressor |
CN101105174A (en) * | 2007-07-06 | 2008-01-16 | 薛亮亮 | Low-power consumption rolling piston type refrigerating compressor |
Also Published As
Publication number | Publication date |
---|---|
ZA201201887B (en) | 2013-05-29 |
CA2774107C (en) | 2014-06-10 |
KR101290849B1 (en) | 2013-07-29 |
AU2010297740B2 (en) | 2014-06-05 |
KR20120051739A (en) | 2012-05-22 |
US8684713B2 (en) | 2014-04-01 |
MY179758A (en) | 2020-11-12 |
CN102022320A (en) | 2011-04-20 |
AU2010297740A1 (en) | 2012-04-19 |
JP5480387B2 (en) | 2014-04-23 |
JP2013505391A (en) | 2013-02-14 |
CA2774107A1 (en) | 2011-03-31 |
CN102022320B (en) | 2013-01-09 |
US20120189481A1 (en) | 2012-07-26 |
EP2481929A1 (en) | 2012-08-01 |
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